Proportional pressure-regulating valve

ABSTRACT

The invention relates to a proportional pressure-regulating valve ( 10 ) for actuating a first fluid connection (f 1 ) from a working connection (A) to a tank connection (T) and a second fluid connection (f 2 ) from a supply connection (P) to the working connection (A), comprising a regulating piston ( 14 ), which is guided in a displaceable manner in a valve housing ( 12 ) and opens the first fluid connection f 1 ) and closes the second fluid connection (f 2 ) when in at least one first position, and closes the first fluid connection (f 1 ) and opens the second fluid connection (f 2 ) when in at least one second position, is characterized in that the regulating piston ( 14 ) can be displaced from a first position into a third position when the first fluid connection (f 1 ) is open by the total differential pressure produced when fluid flows through, and that when the regulating piston ( 14 ) is in the third position, the first fluid connection (f 1 ) is opened with an enlarged opening cross section compared to the first position and the second fluid connection (f 2 ) remains closed.

The invention relates to a proportional pressure-regulating valve for controlling a first fluid connection from a working connection to a tank connection and a second fluid connection from a supply connection to the working connection, comprising: a valve housing having the working connection, the tank connection and the supply connection, a regulating piston guided displaceably in the valve housing, which opens the first fluid connection from the working connection to the tank connection and closes the second fluid connection from the supply connection to the working connection when in at least one first position, and which closes the first fluid connection and opens the second fluid connection when in at least one second position, a restoring device holding the regulating piston in the direction of a respective first position, and an actuating device for displacing the regulating piston against the restoring force of the restoring device in the direction of a respective second position.

Proportional pressure-regulating valves are used, for example, in mobile working machines for the electrohydraulic controlling of clutches. When actuated or engaged, these clutches are initially pressurized with fluid pressure until the respective clutch disk reaches or contacts the respectively associated contact surface. The clutch pressure required to overcome the spring forces assumes comparatively small values below 2 bar. An additional increase in the clutch pressure results in the kind of forces on the clutch disks or clutch linings which then enable a torque to be transmitted by means of friction.

In the case of directly controlled proportional pressure-regulating valves, magnets having large working strokes are used to open or release a maximally large flow cross section as an opening cross section for the respective fluid connection. If these large and comparatively cost-intensive magnets were to be replaced by smaller cost-effective magnets as actuating devices with equal force, the linear power-stroke range would have to be shortened accordingly. Otherwise, this would inevitably mean that when actuating the actuation device, such as when energizing an electromagnet, in order to open the second fluid connection from the supply connection to the working connection, a large spring force or restoring force would have to be initially overcome, and that the linear P-I characteristic curve of the proportional pressure-regulating valve would be achieved in a kind of “jump start” when the spring force or restoring force is exceeded as a result of the magnetic force. This could result in a “jerky”, delayed start-up of the working machine, which is undesirable for the working machine in mobile applications.

Thus, the object of the invention is to improve the function of a proportional pressure-regulating valve for electrohydraulic controlling of a clutch, such that magnets having a shortened linear power-stroke range may be used and an irregular, in particular a sudden, start-up behavior may be avoided.

This object is achieved by a proportional pressure-regulating valve having the features of Claim 1 in its entirety. A proportional pressure-regulating valve according to the invention is distinguished by the fact that, when opening the first fluid connection, the regulating piston is displaceable from the respective first position to at least one additional third position as a result of the overall differential pressure present at the regulating piston, and that in this respective third position of the regulating piston, the first fluid connection having an enlarged opening cross section compared to the respective first position is opened and the second fluid connection remains closed. According to the invention, a respective third position of the regulating piston, which increases a fluid flow to the tank connection or enlarges the first fluid connection, is attainable by also using the differential pressure that occurs during a flow to or flow through the proportional pressure-regulating valve, more precisely the regulating piston, from the working connection to the tank connection to move the regulating piston. Through the respective third position, a kind of rapid discharge function for a hydraulic consumer, such as a clutch, connected to the working connection is implemented in a proportional pressure-regulating valve according to the invention.

The differential pressure expediently engages a piston surface of the regulating piston which, arranged rearward, faces the actuating magnet. Thus, the regulating piston is moved from a first to a respective third position by a restoring force applied by the restoring device, while including the fluid differential pressure present at the regulating piston.

In one preferred embodiment of the proportional pressure-regulating valve according to the invention, the regulating piston is tubular, preferably in the shape of a tube cylinder, constructed with an internal space and includes fluid passages for the respective fluid connections passing through the internal space, wherein at least one passage associated with the respective connection is constructed in the valve housing in each case, and wherein each of the passages associated with the supply connection and the tank connection are, depending on the position of the regulating piston in the valve housing, fluidically connected through the corresponding fluid passages to the internal space, or separated therefrom in a fluid-impermeable manner, depending on the respective regulating position of the regulating piston.

As normally constructed, the fluid passages associated with the supply connection and the tank connection are preferably regularly formed and arranged in a longitudinal section of the regulating piston. In the respective first position of the regulating piston, the fluid passages are arranged in relation to the valve housing in such a way that the first fluid connection from the working connection through the internal space, through the attributable fluid passages and the attributable passage in the valve housing to the tank connection is opened. Thus, in at least one of the first positions of the regulating piston, the at least one passage in the valve housing associated with the supply connection is separated in a fluid-impermeable manner from the internal space of the regulating piston and, thus, the second fluid connection to the pressure supply is closed. Correspondingly, in at least one of the second positions of the regulating piston, the first fluid connection to the tank is closed and the second fluid connection to the pressure supply is opened.

The fluid passage in the regulating piston associated with the working connection and the corresponding passage in the valve housing are advantageously arranged on an underside of the proportional pressure-regulating valve. This configuration results in the advantage of a particularly compact construction of the proportional pressure-regulating valve, wherein the actuating device is expediently arranged on an upper side of the proportional pressure-regulating valve opposite the working connection.

When actuating the actuating device of the proportional pressure-regulating valve, for example, by energizing an electromagnet, the regulating piston is displaced from the respective first position to a respective second position. When switching off the actuating device, on the other hand, the regulating piston is displaced back to the respective first position, inter alia, by the restoring force applied by the restoring device. The restoring device may be a spring element, in particular a compression spring surrounding the regulating piston. The actuating device comprises for example an electromagnet having a linear power-stroke range. In addition, the regulating piston, depending on the fluid pressure present at the piston, is engaged by a differential pressure, which results from the varying surface formation on the graduated regulating piston. Thus, a annular differential pressure surface is provided on the outer circumference of the graduated piston, the pressure activity of which results from the difference between the largest outer circumference of the regulating piston in the region of the working connection and an average outer circumference in the rearward region of the regulating piston facing the actuating device, wherein the differential pressure area between these two aforementioned outer diameters, which delimit corresponding surface areas, is implemented as a further gradation of the regulating piston.

If, according to the invention, the regulating piston is displaced to one of its third positions, the opening cross section for the first fluid connection becomes larger than in its respective third position. This has the advantage that, when switching off, in other words, when terminating the actuation of the actuating device, the fluid pressure through the appropriately occupied respective third position and the opening cross section enlarged in this manner may be guided in a kind of rapid discharge function of the proportional pressure-regulating piston according to the invention from the working connection back to the tank connection.

It is further advantageous that the restoring device engages the regulating piston via an intermediate element, that the intermediate element abuts the regulating piston in the respective first position of the regulating piston, and that the regulating piston in its respective third position is spaced apart from the intermediate element. The intermediate element preferably encompasses the regulating piston at least partially and/or is annular, particularly preferably disk-shaped. A preferably annular piston stop may be formed on the regulating piston and a preferably annular housing stop for the intermediate element may be formed on the valve housing.

Once the appropriate amount of fluid is recirculated from the working connection to the tank connection, the pressure difference and, correspondingly, the effective pressurization of the regulating piston drops to zero. The regulating piston at this point is in an indifferent state, from which with a small actuation force it may be guided back to the respective first position, i.e., in abutment with the intermediate element, during renewed actuation or switching on of the actuating device, typically in the form of an electromagnet. Once abutment, i.e., contact with the intermediate element and consequently with the restoring device is achieved, the actuating device, such as the electromagnet, is in the respective linear range and the corresponding P-I characteristic curve may be traversed from the start, as a result of which any sudden irregularity caused by the clutch device during start-up of a working machine or vehicle may be avoided. Ultimately, according to the invention, the use of a cost-effective magnet having a small linear stroke range is possible without restriction, if an additional movement of the regulating piston from the first to at least one additional third position is made possible by means of fluid pressure, more precisely, by means of the required differential pressure.

The invention further comprises a valve assembly having a proportional pressure-regulating valve according to the invention and a hydraulic consumer, such as a clutch, connected to the working connection of the proportional pressure-regulating valve.

Additional advantages and features of the invention arise from the figures and the following description of the drawing. The aforementioned and the additionally cited features may be implemented according to the invention in each case individually or in arbitrary combinations with one another. The features shown in the figures are purely schematic and not meant to be to scale, in which

FIG. 1 shows a partial section through a proportional pressure-regulating valve according to the invention;

FIG. 2 shows an enlarged detail from FIG. 1; and

FIG. 3 shows a P-I characteristic curve for a proportional pressure-regulating valve according to the invention compared to a conventional solution.

FIG. 1 shows a partial section of an elongated, largely cylindrical proportional pressure-regulating valve 10, which includes a valve housing 12, a regulating piston 14, which is linearly displaceable in the valve housing 12, and three fluid connections, a first fluid connection designed as a tank connection T, a second fluid connection designed as a supply connection P, and a third fluid connection designed as a working connection A. An actuating movement B of the regulating piston 14 is caused by an actuating device 16 comprising an electromagnet capable of being energized. During the actuating movement B, a restoring device 18, designed as a compression spring, on the end of the valve housing 2 associated with the working connection A opposite the actuating device 18, is at least partially compressed or, in other words, an actuating movement B of the regulating piston 14 requires overcoming a restoring force applied by the restoring device 18. If the actuating device 16 engaging the regulating piston 14 is no longer actuated, for example, the electromagnet is no longer energized, the regulating piston 14 is returned to its original position in accordance with a restoring movement R caused by the restoring device 18 and counter to the actuating movement B.

Depending on the state, in other words placement or position, of the regulating piston 14 in the valve housing 12, a first fluid connection f1 from the working connection A to the tank connection T or a second fluid connection f2 from the supply connection P to the working connection A is at least partially opened or closed. For this purpose, fluid passages 20 are provided in a longitudinal section of the tubular regulating piston 14 which, in accordance with the state of the regulating piston 14, open the respective fluid connection f1, f2. From the working connection A, the first fluid connection f1 leads through an internal space 21 of the regulating piston 14 and through the fluid passages 20 to a tank connection T, comprising at least one passage 23 _(T) in the valve housing 12. The second fluid path f2 leads from a supply connection P, comprising at least one passage 23 _(P) in the valve housing 12, through the fluid passages 20 and the internal space 21 of the regulating piston 14 to the working connection A, if the regulating piston 14, as seen in the direction of FIG. 1, moves by means of a displacing movement downward against the action of the compression spring 18, whereupon the previously existing fluid path f1 according to the depiction in FIG. 1 is then closed.

The restoring device 18 does not directly engage the regulating piston 14, but rather a disk-like intermediate element 22 which surrounds or encompasses the regulating piston 14 and is able to move synchronously with the latter. A piston stop 26 is provided on the regulating piston 14 for transmitting the restoring force from the intermediate element 22 to the regulating piston 14, as depicted in FIG. 2 magnified in a size ratio of 10:1. The piston stop 26, like a comparable housing stop 24, is formed as an annular surface on the valve housing 12. In FIG. 2, an arrow indicates that the restoring device 18 causes a corresponding movement of the intermediate element 22, and that the restoring movement R of the regulating piston 14 is caused indirectly as a result of the intermediate element 22 abutting the piston stop 26.

In the arrangement shown in FIG. 2, the regulating piston 14 is situated above one of its second potential positions, into which the former has been guided in an actuating movement B caused by the actuating device 16. In accordance with the spacing shown in FIG. 2 between the intermediate element 22 and the housing stop 24, the second fluid connection f2, delineated by dashed lines in FIG. 1, from the supply connection P to the working connection A is at least partially opened. The second position corresponds to the filling of a hydraulic consumer connected at the working connection A with fluid from supply connection P. A bore 27 is formed in the regulating piston 14, exiting in the radial direction from the internal space 21 at the end of the regulating piston 14 opposite the working connection A. An additional passage 23 _(T)′ associated with the tank connection T is also formed in the valve housing 12. An additional second fluid connection f2′ in the position shown in FIG. 1 leads from the working connection A through the internal space 21 and the bore 27 of the regulating piston 14 to the rear side thereof and in the process arrives at an annular surface 28 formed in gradations in the regulating piston, which allows for a leakage connection with the tank pressure at the point 23 _(T)′ and moreover forms a stop for the upper regulating position of the regulating piston 14 as a result of the annular surface 28 interacting in this region with a corresponding projection on the inside of the valve housing 12. The fluid pressure on the rear part of the regulating piston 14 is registered via the above described fluid path, and the leakage flows during operation of the valve-like regulating piston 14 can be discharged through the fluid connection f2′ to the tank connection in the form of the passage 23 _(T)′ toward the tank side T. Sieve elements 25, which retain any impurities from the fluid emanating from the pressure supply side P flowing into the second fluid connection f2 in the proportional pressure-regulating valve 10, may be arranged in the region of the passages 23 _(P) associated with the supply connection P.

To “discharge” the hydraulic consumer, the energizing of the actuating device 16 designed as an electromagnet is discontinued and the regulating piston 14 is moved from the second position back to the first position in accordance with the restoring movement R. In this first position of the regulating piston 14, the intermediate element 22 abuts the housing stop 24, and the first fluid connection f1 from the working connection A to the tank connection T is again opened and the second fluid connection f2 is closed. During the restoring movement R, the restoring device 18 engages the piston stop 26 of the regulating piston 14 via the intermediate element 22.

In the proportional pressure-regulating valve 10, a third regulating position enlarging a fluid passage to the tank connection T or respectively the first fluid connection f1 is implemented according to the invention in that the differential pressure that occurs when fluid flows through the proportional pressure-regulating valve 10, more precisely the regulating piston 14, from the working connection A to the tank connection T also acts on the regulating piston 14. The actively pressured surface that also serves to actuate the regulating piston is formed from the difference between the surfaces F2 and F1 according to the depiction of FIG. 1, wherein the mentioned difference corresponds to the size of the sector or differential surface 28. The surface F2 in this case corresponds to the largest outer diameter or largest cross sectional surface of the regulating piston 14 in the region of its free front end, which may be abutted by the previously mentioned intermediate element 22. In contrast, the additional surface F1 is the cross sectional surface of the regulating piston 14 in its rearward region reduced by the differential surface 28. The corresponding differential pressure or fluid pressure is available when recirculating fluid from the working connection A back to the tank connection T, for example, when disengaging a clutch associated with the proportional pressure-regulating valve 10. The respective third state or position of the regulating piston 14 is referred to as a “range-extender” in accordance with the stroke increase. In a third position of the proportional pressure-regulating valve 10, an enlarged opening cross section for the first fluid connection f1 is opened in order to empty a hydraulic consumer connected to the working connection A, for example, when releasing a clutch. This enables a rapid discharge function of the hydraulic consumer, for example, a rapid separation of the clutch. The maximal third position for the regulating piston 14 is set via an additional housing stop 24′, which is formed as an annular surface on the valve housing 12, as shown in FIG. 1.

Once the emptying or discharging of the working connection A to the tank connection T is completed, the differential pressure is eliminated and thus the force effect on the circular ring surface 29 on the regulating piston 14 which, as a result, is in an indifferent state. FIG. 3 shows a P-I characteristic curve for the proportional pressure-regulating valve 10 shown in FIGS. 1 and 2. When further actuating the actuating device 16, such as energizing the electromagnet, the regulating piston 14 is initially guided from the indifferent state back to the respective first position, in other words, in contact with the intermediate element 22. A small force of the actuating device 16, designed as an electromagnet, is sufficient to move the regulating piston 14 back into contact or abutment with the intermediate element 22 formed as an annular disk. Once contact with the intermediate element 22, and thus with the restoring device 18 designed as a spring element is achieved, the actuating device 16 is situated in its linear range and the P-I characteristic curve may be traversed without jump start, as delineated in FIG. 3 by dashed lines for known solutions. The fluid pressure p guided via the second fluid connection f2 from the supply connection P to the working connection A increases linearly with the actuating current I for the actuating device 16 designed as an electromagnet. 

1. A proportional pressure-regulating valve (10) for controlling a first fluid connection (f1) from a working connection (A) to a tank connection (T) and a second fluid connection (f2) from a supply connection (P) to the working connection (A), comprising: a valve housing (12) having a working connection (A), the tank connection (T) and the supply connection (P), a regulating piston (14) guided displaceably in the valve housing (12), which opens the first fluid connection (f1) from the working connection (A) to the tank connection (T) and closes the second fluid connection (f2) from the supply connection (P) to the working connection (A) when in at least one first position, and which closes the first fluid connection (f1) and opens the second fluid connection (f2) when in at least one second position, a restoring device (18), which holds the regulating piston (14) in the direction of the respective first position, and an actuating device (16), which displaces the regulating piston (14) against the restoring force of the restoring device (18) in the direction of the respective second position, characterized in that the regulating piston (14) is displaceable from the respective first position to at least one third position by the total differential pressure produced when fluid flows through, and in the respective third position of the regulating piston (14), the first fluid connection (f1) is opened with an enlarged opening cross section compared to the respective first position and the second fluid connection (f2) remains closed.
 2. The proportional pressure-regulating valve according to claim 1, characterized in that the regulating piston (14) is tubular, preferably in the form of tube cylinder having an internal space (21) and fluid passages (20) for the respective fluid connection (f1, f2) leading through the internal space (21), that in each case at least one passage (23 _(P), 23 _(T), 23 _(T′)) associated with the respective connection (A, P, T) is formed in the valve housing (12), and that the fluid passages (23 _(P), 23 _(T)) associated with the supply connection (P) and the tank connection (T), respectively, are fluidically connected to or fluidically separate from the internal space (21) through the corresponding fluid passages (20) as a function of the state of the regulating piston (14) in the valve housing (12).
 3. The proportional pressure-regulating valve according to claim 1, characterized in that the fluid passage in the regulating piston (14) associated with the working connection (A) and the corresponding passage in the valve housing (12) are arranged on an underside of the proportional pressure-regulating valve (10).
 4. The proportional pressure-regulating valve according to claim 1, characterized in that when fluid flows through the regulating piston (14) depending on the fluid pressure present at it, a differential pressure is present at the regulating piston (14) which results from the different surface formation on the graduated regulating piston (14), wherein the outer circumference of the graduated regulating piston (14) is provided with an annular differential pressure surface (28), the pressure effect of which results from the difference between the largest outer circumference (F2) of the regulating piston (14) in the region of the working connection (A) and an average outer circumference (F1) in the rearward region of the regulating piston (14) facing the actuating device (16), and that the differential pressure surface (28) between these aforementioned outer circumferences (F1, F2) is implemented as an additional gradation of the regulating piston (14).
 5. The proportional pressure-regulating valve according to claim 1, characterized in that the restoring device (18) engages the regulating piston (14) via an intermediate element (22), that the intermediate element (22) abuts the regulating piston (14) in the respective first position of the regulating piston (14), and that the regulating piston (14) in one of its third positions is spaced apart from the intermediate element (22).
 6. The proportional pressure-regulating valve according to claim 5, characterized in that the intermediate element (22) encompasses at least partially the regulating piston (14) and/or is annularly shaped, particularly preferably disk-shaped.
 7. The proportional pressure-regulating valve according to claim 5, characterized in that a preferably annular piston stop (26) is formed on the regulating piston (14) and a preferably annular housing stop (24) for the intermediate element (22) is formed on the valve housing (12).
 8. The proportional pressure-regulating valve according to claim 1, characterized in that the restoring device (18) is a spring element, in particular a compression spring encompassing the regulating piston (14).
 9. The proportional pressure-regulating valve according to claim 1, characterized in that the actuating device (16) comprises an electromagnet having a linear power stroke range.
 10. A valve assembly having a proportional pressure-regulating valve (10) according to claim 1, and a hydraulic consumer, such as a clutch, connected to the working connection (A) of the proportional pressure-regulating valve (10). 